Fuel pump for internal-combustion engines



' epto s7 L.- ILLMER FUEL PUMP FOR INTERNAL COMBUSTION ENGINES Filed April 19, 1918 3 smem-smwx Jaws/11mm $044135 a9llmer wamm Sept. 23 1924.

' 1.. ILLM ER FUEL PUMP'FOR INTERNAL COMBUSTION ENGINES Filed April 19. 1918.

3 Sheets-Sheet 5 7 z Z AN Z 1 A l Patented Sept. 23, 1924. i

.. soazee LOUIS ILLMER, or commann, NEW YORK.

FUEL your FOR INTERNAL-COMBUSTION ENGINES.

Application filed April 19, 1918. Serial-No. 229,556.

To a7Z whom it may concern: p

Be it known that I, LOUIS ILLMER, a citizen of the United States, and a resident.'of Cortland, in the county of Cortland and State of New York, have invented a new and useful Improvement in Fuel Pumps for,

Internal-Gombustion Engines following is a specification.

My invention relates to high pressure injection pumps for liquid fuel engines, and its 'ohject is to provide a device which, without the use of compressed air, will effect a high velocity discharge through 'a of which the of the. engine speed, and will also effect a "sharp .cut-ofl' action which will insure againstany drip formation to the dischargingfispray being injected into the engine cylinder. r

. Fig. 7 represents a sectional view taken on line 7 --7,'Fig. -3.

Fig. 8' represents the same view .as Fig;

3 but shows the discharge regulating means in set position for minimum? dicharge and the pump plunger in its up stroke. I

Fig. 9 represents apart sectional view taken on'line 9-9, Fig. 10. 'Fig. '10 "s a similar view to Fig. 8' but shows the discharge regulating means set formaximum discharge.

Like numerals refer to like parts throughout the severalviews of the drawings. ractical size of nozzle'o enin regardless P P s c.

Anotherobject is to provide a liquid fuel" injecting device for highpressure oil engines whichlpossesses regulatable means for varying the amount of fuel to be injected intothe cylinder-and regulatable timing means for varying the timing of injection according as the operating needs of the engine may require.

. Still another object is to provide a device as above described, which is equally applicable to reversing types of internal combustioneiigines as well as to non-reversing engines.

- Theg'terms employed herein are used in the generic and descriptive senseito desig nate the'elements illustrated, and are therefore not specifically intended asterms: of limitation.

Referring to the accompanying three (3) sheets of drawings: 1 l.

Fig. 1 diagrammatically represents an engine equipped with my device Fig. 2 represents a right elevational view The numeral 20 represents inits entirety ahighpressure oil engine in which 21 is the power cylinder, 22 the crank-shaft and 23 a type of spray nozzle ordinarily used for the solid injection of liquid fuels, which dis- I charges into'the combustion chamber 24 of the cylinder.

25 represents a rigid guide member which may be made integral with an engine part,

chamber 28. The pump casing 27 is as the base, or rigidly secured thereto, a ecording as may be desired. 26 is a supplybase or reservoir for the pump casing 27 whichis provided with the pump chamber 28 communicating with the supply chamber 29-of the supply base. 26 through the automatic suction valve 30 which is preferably of the non-return type. The pump casing 27is preferably provided with the bores 31 and 32 in the former of which is slidablyfitted the supporting and'adjusting, guidemember 33. which rides on the regulating eccentric 34 operating within the pumfp pre erably provided with the slots 35 and 36 through which the floating-lever-37 operates and which lever is pivotally secured at one end to the forked guide member 33, as

"shown, with the other end'projecting freely .within the bore32, and is normally held ofFig. 1, showing some of :the operatingmec'hanisms of my device-in section. v

' Fig. 3 represents a sectional view taken on line 3- 3 Fig. 2, showing the discharge regulating means in mid=position and. the

. pump in its suction stroke.

Fig. 4 represents a similar view to Fig. 3

but shows the pump plunger in its extreme Y upT position in the down position b v the light expansion *s rin 38 provided for the purpose, as

shown in Fig. 3. y 40 represents a tapered umpplunger bushing which is secured to the casing 27 in the tapered section provided therefor hyfithe take-up gland 41 which is screwed to the casing 27 and provides a' type of pump plunger 42 as shown.

stuffing box about the floating or impulsion plunger is intended to work reasonably free through said stuffing box so asnot to inter. fere unduly with the action of its'inter Inediary impulsion drive, as will be ex- The plained hereinafter. The tapered member is perforated with the transverse holes 43 which register with the main discharge casing ports 44 and 45.

The regulating eccentric is'p'reterably made integral with the spindle 46 which rotatably operate's'within the gland 47 through the regulating arm 48 which is Socured to said spindle 46. The top of the casing 27 is provided with the auxiliary relief valve plug 50 which is rigidly secured thereto and which in turn is provided with the relief valve 51 which seats at 52 and has its spindle 53 extending into the pump chamber 28' and positioned in the plane of the floating-lever 37 for engaging ther with, as will behereinafter explained. The plug50 is provided with the intake and discharge ports 54-and 55, respectively, and houses the impulsion spring 56 which acts against the'valve'51 to seat the same noradjusting'scr'ew 58 into set position with the plug 50, I

lVithin the rigid guide member 25' operates the reciprocating pump member 63 which houses the expansion spring 64, acting against .the floating pump plunger 42 through the slidable guide plug 65 and is provided with the arced shoe or link block 66. which .may' be rigidly secured thereto or made integral therewith, according as may be desired. The floating pump plunge .42-is provided 'with the valve recess 61 towards the top end thereof. while the lower end is provided with the shoulder or flange 68 which floatingly couples the plunger 42 with the reciprocating member 63 through the regulatable coupling member'GQ which is adjustably securedto said reciprocating member 63 as shown. 70 represents a stop rod to limit the spring deflection and is housed with n said reciprocating member 63 and is preferably rigidly securedthereto.

In the construction shown the arced shoe 66 sl dably carries the timing and reversmg arc or link sector 71 which is pivotally member 73 which is actuated by the eccentric 74 keyed or otherwise coupled prefer ablv to the crank-shaft 22 for rotating therewith. e v

The are 71 is pivotally coupled to the con- I necting link 75 which in turn is pivotally coupled to the operating lever 76 which is fulcrumed at 77 to the notched or toothed into set position through any suitable look ing means, as the spring-held latch shown in Fig. 1 for example. It is apparent that instead of the described link construction, the same results may be attained by means of a Stephenson or similar type of reversing gear to change the stroke of the reciprocating plunger-42 and provide for varying the tim- I ing of the main discharge port 44.

The main discharge port 45 of the pump casing 27 connects with-th'einjecting valve 23 by means of the pipe 80, and'the injectregulating eccentric 34 according to the speed of the engine.

Having thus described the parts of my invention in detail, the manner in whichthe same operates is as follows:

First, it will be observed that the setting of the timing lever 76 in the full line posi-' tion shown in Fig. :1 for forward running of the enginedndicated by the arrow marked F, yields a cracking or opening of the plunger valve when'the eccentric center C reaches a point in advance of the head end dead center position as shown in Figs. 1 and 8. Therefore, it must be understood that any setting of the timing lever 76 between the full line position shown in Fig. 1 and the dotted position shown in sa d figure and indicated X for forward running of the engine, will yield an earlier crackingof the plunger valve of the device than that occasioned by the full line setting of said lever 76 and similarly it follows for forward runn ng of the engine that any setting of the lever '7 6 beyond the full lineposition shown in Fig. 1 in the opposite direction on the arc or quadrant 78 (as for example the dot- ,ing valve is provided with the check-valve lOO ted position .Y) will retard the time of opening of the plunger valveof the device and will allow for a later injection.

For reverse running of the engine indicated by the arrow marked B, Fig. .1. the

coupled at 72 with the operatingeceentric full line position shown'insaid figure will yield the same relative time of opening for the plunger valve 'as occurs. in forward running of the engine. but advanc'ng the lever towards the X p gsiti oni-{will yield late injection, while ad cing the lever 76 towards the Y positi will yield a leading or earlier injection. I

Assuming-for example that the compresarc-7 8 to which the lever 76 may be locked sion pressure in the combustion chamber 24 is 300 lbs. against whichm 'deviceinjects;

the liquid fuel and that the esi'red pressure to be maintained in' the pump chamber 28 is set at say 2000 lbs. per sq. inch or'over,

then it will be understood'thatasui'table spring 56 must be employed sufiicientto hold the valve 51 seated against the pressure required in the pump chamber 28. The spring 64 must be designed t cau'se the'same to 10 compress under the desired pressure'in the pump "chamber 28(as shown in Fig; 8), but

111 any event must be sufiiciently stiff to fur-'-.

nish the impelling kick to the plunger such that the spring drives said plunger be.-

yondyits n ormal limit otdischarge-strobe spring 56' is comparatively light butsuiiicient nevertheless to withstand the desired V erably so located new take.

.- The regulating arm pressure in the pump chamber, g'while on the other hand the spring 64 is relatively stifier and capable of forcing'the plunger 42 to liftflthe relief or auxiliary discharge valve'x51 thr ugh the floating lever 37 against the pressure of the spring 56. will also be understood that the port 54 leading to the bleeder valve seat 52 is prefany Zentrapped air that may accumulate at the highest point in the pumpchamber andthus prevent the plunger from becoming airbound.

eccentric 34 may be hand-operated if desired, and may be provided with 'lockin means, as a-notched locking arc (not shown for holding the sa e in set position. lt is preferable, however wl'ierever possibl'e' to couple said arm 48 with'the governing mech-. anism (not shown) of the engine, as by means of the link'ST, for automatically reg ulating the supply eccentric according to" the engine load; the arm 48having a radius of actionfrom the minimum supply position; represented by the dottedposition of the arm, Fig. 9, which corresponds to the eccentric setting in Fig. 8. to the maximum supply position shown in Fig.- 9 (full lines) I which corresponds to the GCCGIitI'lQ-SBIlZlLlDg.

shown in Fig. 10..

uming that the engine is o iate Now ass ing in the forward direction, represented by the arrow marked F Fig.1, withthe timing lever set in mid or full line position shown in said-figure, that the regulating eccejntric' is set in the mid position ,corresponding to the settlngshown infFigsJ3', 4 and 7, and also that the supplychamber 29 is kept supplied with liquid fuelunder a' fixed initial pressure head, then the-device operates in the following manner: The suction stroke, as is understood, is the down stroke-of the reciprocating member 8?) which .1s actuated by theeccentric member 7 3 and carr1es the floating plunger 52.

Fi g. 3 shows the device in the suction stroke, where it will be'noted that the plunger and relief valvesjare both closed, while the suc- .Thesuction stroke of thedevice fills the Y pump'chamber 28 with the'liquid fuel used topper-ate the engine.- As soon as the reciprQcating member-LGS completes its suction stroke it start on its compressionor up stroke as shown in Figs. 8 and "10, and

the suction valve 3O closes. In this compres sion-strokc of the device it will be noted that the pressure inthe mp'chamber rises to the required-point say-2000 lbs.) be 0nd which but 'previous to the opening 0 the .plu'ngeror mainldischarge'valve of the device, the-auxiliary OI. 'reliefvalve 5-1 (because of. the incompressibility ,of'the liquid in the closed pump chamber 28) iscuused to unseat (Fig. 10) sufficient to allow. a bleeding action to take place, resulting in a limited discharge through the port 55 of the plug 50, from where the discharge drains back through the pipe tlQ'to thefniain oil supplyreservoir. (notQshown). 'Dur ing this v periodof the compression stroke, it will. 48 which operates the also be noted that the fiuidpressure loadon plunger 42 acting through the sli dable guide between the flange 68. of the plunger 42 and the coupling member 69 forthe supplemental reaction or kick ofthe'plunge1',"wl1i'ch will be more fullyexplained. 1:

It is further pointed out that thespring 63 is'to be made "stiff enough to c arify the oil pressure load imposed upon the plunge without excessive I deflection "andv thatgthc .plug' 65-should not. be allowed tobottom upon stop. rod 70 before themaximumdesired pressure has 3 been reached in the ticity tram overload. .It isfa'pparent that pump chamber. thus far alltimes keeping 4 lsaid-spring fully. balanced with respect to the'oil pressureload acting 'on theplunger. "The st'op rod'70 is-intendedto protect the spring 63 against impairmentof'its'elasl deflection" may. be stillf properly limitedso'- as. to holdthej lunger inv its required posi- -tion for the,pu,poses intended even though the stop rod 70 is e'litirfely"dispensed with.

[The position of. the plunger42 and the -reciprocatingmember 63; as shownin F ig.

.8, corresponds to the position of the driving eccentric 7 {shown in 'Fig. I, in which view it will be seen that the center C of tl'ie-eccentric 74 for forward or F runningdh rection ofthe engine is approaching its dead center position but.in advance of said head dead center position, and in that position .(as shown in Fig. 8) the plunger or main discharge, valve is justcracking open.

- Therefore, the remainder of the eccentric ger valve, which opens'the pump chamber" stroke willlift the plunger 42 the short dis tance L on the eccentric'circle (Fig. 8),

during which lift the plunger valve will rc main open. With the openingof the'plun-v to th'eengine cylinder, theauxiliary or re lief valve-51 automatically closes and stops the bleeding action above referred to and the oil in the pump chamber, which is under a much higher pressure than the pressure in the combustion chamber, forces its way through the pipe 80 and is finally injected in spray form at a high velocity into the combustion chamber 24 through the injection nozzle23. Thus it will here be observed that the device is designed to provide a positive opening ofthe main discharge valve of the pump under the direct action through' the plunger valve by the occur-' a of the operating eccentric 74, as alreadyex-' 'pla'ined.

Supplementary to that action the device said normal period, together with a fur- 'ther accelerating drive onthe oil discharge rence of an additional length of stroke-to th'epump plunger which is due to the independent reaction of the spring 64 in the reciprocating member 63, taking place in the shape of a kick against the plunger42 through the distance K (Fig. 8) when the reciprocatingmember 63 nears or reaches tithe? top of it s stroke. It will thus be here noted that'the plunger 42 is of the impulsion l'di'scharge stroke by. the. operating eccentric and that the'same is actuated directly in the first instance on its compression and 74, and that in addition thereto it is further actuated during said'str'oke by the reaction or expansion of the spring 64 which kicks against it with-appreciable force and provides the functions above stated.

The steady high pressure behind the spray nozzle resulting from the follow-up acaction with a commercially practicable nozzle j orifi'cefof say 1/64 or larger, even in engines 65 of relatively small bore dimensions.

is designed to prolong the period of open-' ing of the plunger valve beyond the afore- The amount of. forced throughthe main discharge valve 44'. is dependent upon sulting from the actuating gear.,m0vement and the supplementary plunger kick. In

.the 'simultaneous plunger displacement rea variable speed engine'it is preferred to impart the major portion of the plunger displacement required at slow speed by.

means of the plunger kick, while'at-the higher speeds the actuating gear may be made to contribute a larger component of the resultant plunger displacement.

When the spring 64 is compressed load imposed 011 the plunger by the predetermined chamber pressure as previously deby the i scribed, it willbe apparent that the opening of the dischargevalve affords a second independent outlet for the high pressure maintained within the pump chamber prior to the discharge period; Such s'econdpump outlet discharging to the nozzle offers a far lower resistance to the oil than does the loaded bleeder valve when set for a high predetermined pressure. As ;a result of opening the discharge valve, the pump.

chamber pressure will drop somewhat, thus automatically closing the bleeder valve 51 which in turn star ts the release of the energy stored in the spring 64 and allows it to'impart its characteristic impulse to the plunger part. The spring force rapidly drives the plunger forward and ahead of its re- 'tarded gear position whereby the resulting impulse or kick is made to accelerate the plunger movement with respect to the rigid actuating gear movement.

Due to the' yielding drive, the rataat which the plunger is allowed to surge forward is' primarily fixed by the restricted discharge capacity of the nozzle, andis not.

therefore limited to thevelocity imparted by the rigidactnating gear movement.

' The initial pressure maintained behind the nozzle will be slightly lower than the predetermined pressure fixed by the bleeder valve, and this will continue to drop somewhat as the restricted nozzle discharge allows the yielding drive to recover. Since .the displacement capacity of the kick is intended to exceed thenorm'a'l or rated discharge capacityof the pump, it will be furvther evident that during the major portion of the discharge period, the yielding plunger drive serves to crowd the nozzle to the utmost of its discharge capacity and so maintains a nearly uniform. discharge pres-.. sure behind the nozzle during the entire injection period.

It is emphasized thatwithin the range of its rated capacity, my 'fuelpump is intended to utilize only the initial or effective portion-ofits impulsion stroke for the purpose of injectingffuel into the engine cylinder. The end portion of said stroke is pur-' posely discarded. After the pump delivery incense .pressure'has dropped to point where it is still fairly high but no longer capable of producingthe desired efiective atomization of the injected fuel, the chamber pressure issharply-interrupted by means of the by pass valve which then cuts oil the fuel delivery. to the fuel injection nozzle. This valve serves as a supplementary vent for the airthat may "have been. entramed or entrapped in the liquid duel passages and to rid the pump of thepernicious air effects. Unless this is'preven'ted,'the. pump would continue to deliver imperfectly atomized fuel to the injection nozzle until the-confined air pressure had entirely spent itself, notwithstanding that the plunger may already have partially completed its return or suction stroke. By virtue of the described pressure control means, it becomes possible to accurately terminate the period of fuel injection into the engine cylinder when workingwith theiimpulsion type of pump plunger.

Furthermore, the fact that the rate of nozzle discharge is not primarily dependent upon the actuating gear movemen allows a pump of this kind to be run at 510 iv piston speeds without impairing its atomizing ca-,

pacity, and in the case of a four-stroke engins, it is. possible. to 'operate the pump at hall engine speed in unison with the cam shaft and still get a proper nozzle action at" all speedsol the engine.

it is rurther pointed outthat in my high pressure pumping device, a considerably larger amount of oil is sucked from the supply reservoir 26 than is ultimately sent forth to the engine cylinder. The purpose oi this excessplunger displacement is twofold: First, to insure sucking in a surplus amount of solid oil into the pump at all speeds after allowing for any air that may be entrapped with, the oil and, for sluggish lifting; of, the suction valve {and secondly,-

to allow subjecting the oil to apredetermined high pressure prior to the discharge valve opening. Y 7

in connection with the above supply and spraying action of the device, it will now be Gl lPlfilllBClllOW the device is further designedto automatically cut-oil the spray to the cylinder (when the charge, in the cyliuder becomes suthcient) with a marked degree cit suddenness, whereby it. becomes impossible fcrthe spray to forminto drips st the-end of the spraying period. This sudden cutptt action of the spray, is accomplished through the forced opening of the auxiliary or relief valve 51, as is occasioned through the lifting of the floating lever 37 by the plunger' lZ (Fig; l), whereupon the pump chamber 28 is suddenly opened to atmospheric pressure (that being the pressure in the pipe and the oil tlierein'immediately starts to flow through the auxiliary or relief valve against said atmospheric pressure, instead of the much higher pressure of thecombustion chamber. This results in setting up a sudden and sharp drop in pressure in the pipe connections leading .to the spray nozzle and eliminates the drip formation to the high pressure in the spray which otherwise occurs when the spray valve down in the pump chamber has been relieved or: its I pressure.

in my improved construction, the mechanically operated discharge valve is positively held open while the pump chamber is being relieved of pressure,-whereby a di rect communication is maintained during" this period between the nozzle pipe and the relativel liberal vent area afi'orded by the relief vs vs 5L The interval'anol extent of the spraying action and the point o l outoll to the spray is governed by the setting of the regulating eccentric 34 which varies the position of the tulcruming point of lhe lower the fulthe floating-lever 37. cruming point (as Fig. 10) the later the relief valve is forced open by the pump plunger ,42 and consequently the longer the period of spray and the later the point of cutoff; while the higher the fulcrurning point of the'floatingdever 37 (as 8) the earlier the opening of the valve 51, re,

sulting in the shorter period oi spray and an earlier point of cut-0H of pressure 1n the spray valve connection.-

it will thus he observed that by coupling the regulating eccentric 34: with the governing mechanism of the engine that automatically the device will adjustitself to suit the needs .of the engine as to fuel supply.

The fluid discharge sent forth to theengine cylinder'is accurately measured by the com- "pin'ed plunger kick and actuating displacement which is allowed to occur between the time of opening the main discharge port 4:4: and the lift or the relief valve 51. Two

distinct ineansare provided which allow of regulating the oil cllsch'arge from the pump, one residing in the variable timing given themain' discharge valve by the link sector ,71, and the other residing in the floating lever 37,

It will also be observed that the ans relief-or discharge valve til acts in dual capacity; in onecase it acts as a bleeder while the plunger 42 is in its delivery stroke and previous to the opening of the plunger valve, while in the other case itacts to cutoff-the spray at the desired time when the plunger or main discharge valve is open.

1 reservoir, may be used to perform the regulating functions for the pump discharge by breaking the pressure at the spray noz-' zle at a definite but variable point in the plunger discharge stroke. Any suitably vactuated relief valve, controlling thecommunication between the nozzle pipe line 80 and the supply reservoir 2.6, may be used for this latter purpose, in which case such valve remains seated and does not functionuntil after the discharge valve has been opened. 1

1 function of the valve 51 is not an essential It is further pointed'out that the bleeder element in the described type of fuel pump. It will be evident that thebleeder function of said. valve may, if. so desired, be elimi-.

nated since the resilient plunger drive of itself affords a large measure of safety against an excessive pressure arising in the pump chamber. Such a drive at the same time provides a suitable means for securing a predetermined maximum pressure within; the pump chamber prior to the opening of the discharge valve, without necessarily re-.

sorting to the use of a bleeder valve forthis purpose.

i It will also be observed that the valve 51. acts as a safety valve for the device, should the injecting nozzle 23 become clogged through any cause; the spring 56 is adjustable through the adjusting plug 58 and the lock nut 62 may be removed even during the operation of the device to check up the working functions of the same without stopping the engine. The device may be made up as substantial as may be necessary tosuit the particular uses to which the same may be put, and is absolutely reliable practical, overcoming many. of the heretofore objectionable features'common to the ordinary sides in the discharge valve control for re- 7 devices used forthe purpose, and-therefore supplies a long-felt want in thefart. I Finally, it is pointed out that a further important feature of present invention re- .j leasing the impulsion energy stored behind the plunger as used in combination with a bypass device adapted to interruptthe pump chamber pressure. This arrangement admits of breaking the pump chamber pressure either subsequent or prior to the discharge valve opening-and hence an effective and positive plunger ram action is produced irrespective of the relative pump delivery through the-discharge Valve. In the present instanceythe discharge valve and passages leading to the cylinder nozzle may be unrestrictedly opened at any predetermined period and the pump will' contin'ue to freely deliver therethrough Within its rated capacity up to such time that the bypass becomes operative, whereupon theeffective pump delivery will be interrupted although the discharge valve may still remain wide open.

This improved mode of operation'represents a distinct advance over such types of fuel injectors in which the termination of the the timed closure of the discharge valve element; this latter type of' pump involves injecting its fuel delivery through a restricted and partiallyopened-release control for the resilient plunger, which in turn, makes the resulting'plunger kick sluggish engine loads.

While the preferred embodiments of my invention have been described in detail, it will be understood that I do not wishto be limited to the particular construction set forth, since various changes in the form,

material, proportions, and arrangement of.

parts, and in the details of construction may be resorted to without departing from the spirit and scope of the invention or destroyplunger delivery is made dependent upon and less effective, particularly so at light mg any of theadvantages contained in the same, heretofore described and defined in the subjoi-ned claims.

Having thus described my invention in detail, what I claim as new is:

1. A pump comprising a plunger, a suetion valve and a positively opened discharge valve, a relatively rigid actuating gear for reciprocating said plunger, an intermediary resilient drive adapted to yield against said plunger during a portion of the discharge stroke movement of the actuating gear, means for opening said discharge valve to allow said drive to recover and impel the plunger onward, and means adapted to utilize only the initial portion. of the impulsion stroke for .the effective pumpdeliverythrough said discharge valve.

.2. In an internal combustion engine in .,which liquid fuel injected in to achargeof compressedair held within the power cylinder, a fuel pump having a suction and a positively opened discharge valve, a reciprocating actuating partand a driven. plunger part, an impulsion drive acting between said parts,'means to store impelling energy during a portion of the discharge stroke of the actuating part, means for opening said discharge valve to quickly release said energy 1 and inject liquid fuel into the power cylin 'der, and control means adapted to interrupt the pump delivery through said discharge valve prior to the closure thereof. I

3. In a reciprocating pump having a sucti 11 valve, a positively opened discharge Y valve and a plunger part, a relatively rigid actuating gear, an intermediary resilient drive for the plunger part, a bleeder valve to maintain a predetermined pressure with in the pump chamber and serving to store energy in said. resilient drive during a portion of the discharge stroke of the actuating gear, and means for opening the discharge valve to release said energy and impel the plunger part onward.

l. In a reciprocatmg-pump having a suctlon valve, a positively opened discharge valve-and a plunger part, a relativelymigid actuating gear, an intermediary resilient drive for the plunger part, aloaded blee'der valve maintaining a predetermined {pressure Within the pump chamber and serving to store impelling energy in said resilient drive during a portion of the discharge stroke of the actuating gear, means for opening the dlscharge valve to release said energy and impel the plunger part onward, and control means for unloading the bleeder valve at a definite but alterablepoint in the plunger discharge stroke.

5. In a pump having a plunger part and a positively opened discharge valve' a relatively stifi' actuating gear for reciprocating said plunger part, an intermediary resilient drive adapted to yield during the plunger dischargestroke; means for opening said discharge valve to impel the plunger part onward, -means for returning the plunger part with the actuating gear, and bypass means adapted to interrupt the pump delivery.-

6. In a pump having, a reciprocating plunger membeiy a relatively stiil actuating gear, a resihent drive, means for storing impulsio'n energy Within said drive during each dlscharge stroke movement of the actuating gear, a discharge valve adapted to release said energy; a valve gear means for opening said valve, and control means for variably timing the opening of said valve.

7. In a pump comprising a plunger and a chamber havingan inlet and a discharge valve, a relatively still actuating gear adapted to reciprocate said plunger, means ior positively opening said discharge valve, an

auxiliary resilient drive adapted to act against said plunger during the latter portion of its discharge stroke for subsequently impelling the plunger onward to effect a more rapid rate of discharge during the latter part of its stroke, andrcontrol means adapted to interrupt the pump delivery through said dischargevalve prior to the closure thereof.

, 8. In' a pump comprising a recessed plunger member anda ch'amber having'an inlet-valve" and a plunger controlled discharge port, a-relatively stiff actuating gear adapt 7 ed to reciprocate said plunger member and to register the recessthercof with said: d1scharge port and promded W1l3l1 an auxiliary resilient drive adapted to yield prior-to-the registering'o-t said plunger recess and serving to supplementally impel said plunger onward to maintain a more nearly uniform rate "of pump discharge.

9.111 a pump comprising a recessed plunger member. and a chambeifi having aninlet and a plunger controlled discharge port, a relatively 'stiil actuating gearadapted to reciprocate said recessed plunger menr ber andto register the recess thereotivith said discharge port, an auxiliary resilient. drive adapted to yield prior to the register ing of said plunger, and means forvariably' timing the opening of said d scharge port.

adapted to reciprocate said plunger, an

auxiliary or bleeder valve serving to maintaiu the'pnmp chamber at a. preset rmined pressure,v an intermediary resilient drive adapted to yield aga nst said plunger dun ing a portion of its discharge stroke and for accelerating the rate of pump discharge durlng the latter part of the drscharge'stroke through said main discl'iarge'valvc, and 'means for closing said bleeder valve du r-' ing said discharging period,

12, In a pump comprising a plunger and a chamber having an'inlet and a main'dis charge valve, arelativelystitt actuating gear adapted to reciprocate said plunger,- an auxiliary-resilient drive adapted to provide the plungerwvith a limited yielding action during a portionof its discharge stroke, a combined bleeder and relief valve serving in the firs'tinstance to maintain. the pump enamber at a predetermined pressure and subsequently as an auxiliary discharge for said pump, means for opening the main discharge valve, and means for o'penlng sa d combined valve to relieve the pump chamber oi pres (iii lUO

sure and to interrupt the discharge fthrough the main discharge valve.

13'. In a pump comprising a plungeranda chamber having an inletand'main-discharge valve, a relativelyistifi actuating gear adapted to reciprocate "said-plunger, anauxiliary resilient drive, a combined bleeder and relief valve serving in the first insta'nce'to maintain a predetermined pressure in the pump chamber, means for opening the main discharge valve, means for opening the 'combmed-valve to relieve the chamber-of pressure, and a control means/for variably timing said combined valve opening means and adapted to regulatably measure the fluid discharge through the main discharge valve.

14. In a pump comprising a reciprocating.

- plunger and a chamber having an inlet and amain discharge valve, a combinedbleeder and relief valve serving in the first instance to maintain a predetermined pressure in the pump chamber, means for opening the main discharge valve and simultaneously closing the bleeder valve, and means for opening the combined valve to break the pressure in said pump chamber and interrupt the discharge through the main discharge valve,

15. In a pump of the'chara'cter described, a casingmemberhav-ing a supply chambercommunicating with a pump chamber provided with an inlet, a main outlet and an auxiliary outlet, communicating with said supply chamber, a plunger having a flexible 'lating the timeof opening of said auxiliary connection with an actuating gear therefor provided with means for porting said main outlet, means for normally closing said auxil iary outlet,means for mechanically opening said auxiliary outlet, and means for regu' means for actuating said fioatable plunger.

17. In a pump of the character'described,

a casing member having a pump chamber communicating with a supply chamber and provided with an inlet, amain outlet and an auxiliaryoutlet communicating with said. supply chamber, aafloatable plunger provided with means for porting said main outlet, means for normally closing said auxiliary outlet, means engaging with'said plungiary' oiitlet, means for actuating said floatable plunger, and yieldable energizingmeans .forsaid actuating means for furnishing a recovering impulse to the plunger.

1-8. In-a pump of the character described, a casing-member having a-pump chamber provided with an inlet valve, a main plunger valve outlet open to an injecting nozzle, and

an auxiliary -'outlet. open to the source of I supp-ly e pump plunger operating in Said pump chamber'providedwith a valve control for said main outlet, a driving member provided with rigidjand yielding pushing means adapted'toengage with said pump plunger,- a coupling member floatably connecting said punipplunger with said driving member, a valve normally closing said auxiliary outlet, an auxiliary valve lever adapted to be operated by the pump plunger for opening said auxiliary outlet valve, a moveable pivoting member carrying the pivoted endiof said lever, and means for.

changing the position of said vinovealole piv-" 4 a casing member having a pump chamber provided with an inlet valv'eya main plunger valvev outlet. open to an injecting nozzle, and an auxiliary outletopen tothe source of supply, a pump plunger operating in said pump chamber provided with a valve control for said'main outlet, a driving memher provided with rigid and yielding pushing means adapted vto engage with said pump plunger, a coupling member float-v ably and regulatably connectin' said pump plunger with said driving them er, a valve normally] closing said auxiliary outlet, an

auxiliary valve lever adapted to be operated bythe pump'plunger .for opening said auxa 1 moveably pivoting iliary outlet valve member carrying the pivoted end of said lever, meansior changin'g'the position of said moveably, pivoting member, means for actuating'said driving member, and means pump; plunger.

20. ln'a pum having a plunger member,-

for varying the timing operation of said againstsaid member during a portion of thedischarge stroke thereof, means subsequently allowing said drive to recover and impel the plunger member onward, and means to control said plunger impulse.

" 21. In a pump comprising-a plunger memher and a chamber having an inlet and a discharge valve, a relatively stifi actuating gearadapted to reciprocate said plunger, an auxiliary or bleeder valve servlng to maintain the pump chamberatfa'predetermined preser for opening said auxiliary outlet, means sure, an ag ixiliary resilient drive adapted for variably setting the latter meansfor reg f t ulating the timecit opening; of said auxilt'oiyield-a ainst said iplun er during a' ortion ofeits g 'discharge stro e, means su sethe actuating part, control means for open- -r a a 1,509,238

- quently allowing said drive to recover and pump discharge through the impel said plunger onward to acceleratethe discharge valve, and means for closing'said bleeder valve during said discharge.

22. In a fuel pump for aninternal combustion engine, comprising a plunger and a chamber.l1aving a suction anddischarge valve,'.a relatively rigid actuating gear adapted to reciprocate said plunger, operating means ,for'positively opening said dis-.

charge valve an auxiliary resilient drive adapted to yield against said plunger dur- ,-ing a portion of its discharge stroke, and

regulating means for changing the opening 0f said discharge valve with respect to the end of the actuated plunger stroke to variably impel the plunger onward and regulate the fuel discharge from the pump.

23, In a reciprocating pump comprising a positively opened discharge valve, a driven plunger part and an actuaitlng part, a spring drive connection between said parts, means for compressing said 1 spring during a portion of the discharge stroke movement of ing said-discharge valve to release said spring and lmpel the plunger part onward,

said spring being broughtto substantially the same degree of co'mpression prior to its release irrespective of the through said discharge valve.

24:.In a reciprocating pump comprising a positivelyopened discharge valve, a driven plunger part and an actuating part,-a spring drive connection between said parts, means for compressing said spring during a portion of' the discharge stroke movement of said actuating part andfor opening said discharge valve to release said spring and control means for limiting the effective i'mspring.

pulsion movement ofsaid parts with re-. spect to each other. I

25. In a reciprocating pump having a suction and a positively opened main discharge valve and comprising a driven plunger part and an actuating part, a spring drive connection between said parts, an "uxiliary bleeder valve to maintain a predetermined pressure within the pump chamber and servingto compress-said spring during a portion of the, discharge stroke of the actuating part, and means for subsequently opening the main discharge valve to release said 26 In an internal combustion engine, a reciprocating fuel pump havinga suction and adischarge valve and a plunger, a

spray nozzle for admitting fuel into the power cylinder, a conduit connecting the discharge valve with the spray nozzle, an auxiliary valve adapted to relieve said cone dui't of pressure to prevent dripping at the nozzle, means for opening said auxiliary valve at a definite but variablepoint in the pump delivery iliary reliefvalve adapted to bypass into said reservoir and serving to interrupt the pump discharge, a lever adapted to open said relief valve, having a protruding part projecting into the path of said plunger part, and regulatable means for striking said protruding part in a definite but alterable point in thepath of said impelled plunger part.

28. In a reciprocating pump comprising a suction valve and a supply reservoir there for, a positlvely opened discharge valve, a

driven plunger part and an actuatingg'ear .part, a spring drive between said parts,

means for-compressing said spring during a portion of the discharge stroke of sald actuating part, and meang for op pning said discharge valve to release said spring and to impel said plunger part onward; an auxiliary relief valve adapted to bypass into said reservoir and servingto interrupt the pump discharge; a floating lever adapted to open said relief valve, said lever having an end portion projecting into the path of the plunger and adjusting means at its other end portion adapted to alter the position at which said lever opens said auxiliary re-' lief valve.

29. In a reciprocating pump comprising a suction valve and a supply reservoir therefor, a positively opened discharge valve, a driven plunger part and an actuating gear part, a spring drive between said parts, means for compressing said spring during a portion of the discharge stroke of said actuating part, and means for opening said discharge valve to release said spring and impelsaid plunger part onward, an auxiliary relief valve adapted to bypass into said reservoirand serving to interrupt the pump discharge, and mechanical means operating in unison with the plunger part to open said {elief valve subsequent to said spring reease.

30. In a reciprocating liquid fuel pump comprising a suction valve and a supply reservoir therefor, a positively opened discharge valve, a drivenplunger part and an actuating gear part, a spring drive between said parts, means for compressing said ,spring during a portion of the discharge stroke of said actuating part, and means for opening said discharge valve to release said spring and to impel said plunger part onward, anauxiliary relief valve adapted'to bypass intosaid reservoir and serving to interrupt the pump discharge, mechanical 'means operating in unison with the plunger .part to open said relief valve and governing means for the last named mechanism to con- I spring during a portion of the discharge 'trol the delivered pump discharge resulting from the combined gear and impulse inove-.

ment imparted to said plunger part.

31. In a reciprocating fuel pump comprising asuction valve and a su ply reservoir therefor, a positively opene main discharge valve, a driven plunger part and an actuating gear part, a spring drive between said parts, means for compressing said stroke of said actuatingpart and means for opening said dischar e valve to release said spring and impel sai plunger part onward, and anoverflow means to maintain an initial pressure head within said supply reservoir. v

32. In a reciprocating liquid fuel pump discharging toa spray nozzle, a suction valve and a sup ly reservoir therefor, a pump chamber adapted to pump an excess quantity of liquid fuel during each stroke, a positively opened discharge valve commu nicating with said nozzle, a driven plunger part and an actuating'gear part, a s ring 4 said bleeder valve further serving to return drive between said parts, means inclu ing a bleeder valve to maintain a predetermined pressure in the pump chamber and serving to compress said spring during a portion of the discharge stroke of said actuating part,

I the excess portion of such excess liquid fuel suction and a ischarge valve therefor, a

to said reservoir, means for subsequently opening said discharge valve to release said spring and impel the plunger onward whereby a portion of the remaining fuel is sent forth to said nozzle, and regulating means for variably interrupting the nozzle discharge.

33. In a pum having a chamber and a nozzle, a conduit delivering to said nozzle,

a'controlled relief valve adapted to relieve the delivery pressurebehind said nozzle and prevent dribble, means'for opening said re- V lief valve, and means for periodically establishing communication between said chamber and the nozzle during such relief period.

34.'I1i a pump comprising a plunger, a

discharge valve, a nozzle, a conduit delivera l V ing from said'discharge valve to the nozzle,

a-driven plunger partiand an actuating part,

a spring drive acting between said parts, means for'compressing'said spring during a portion of the discharge stroke of the actuating part, means for. opening the disv charge valve to release said spring and impel the. plunger onward, anda bypass valve' adapted to relieve the delivery pressure behind said nozzle and prevent dribble.

35. A pump comprising'a plunger member, a suction valve and a discharge valve, a relatively rigidactuating gear for reciprocating said pliinger member, an intermediary resilient drive adapted to yield against said plunger'member during a portion of the dischargestroke movement of the actuating gear means allowing said drive .to recover and impel the plunge'r'member onward, and control means serving to interrupt the pump delivery pressure prior to the end of the impulsion stroke.

J SGQ In a' fuel pump comprising: a reciprocating actuating part and a driven part.

an iinpulsion. drive acting between said parts, means for storing energy within said set my hand this" fifteenth day of April, 1918."

LOUIS ILLMER.

1 'In testimony whereof, I have hereunto 

